US12435794B2 - Fluid control valve - Google Patents

Fluid control valve

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Publication number
US12435794B2
US12435794B2 US18/563,717 US202218563717A US12435794B2 US 12435794 B2 US12435794 B2 US 12435794B2 US 202218563717 A US202218563717 A US 202218563717A US 12435794 B2 US12435794 B2 US 12435794B2
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Prior art keywords
valve
piston
fluid control
flat surface
control valve
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US18/563,717
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US20240271705A1 (en
Inventor
Hideki Higashidozono
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Eagle Industry Co Ltd
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Eagle Industry Co Ltd
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Assigned to EAGLE INDUSTRY CO., LTD. reassignment EAGLE INDUSTRY CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HIGASHIDOZONO, HIDEKI
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
    • F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
    • F16K31/406—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0466—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with a special seating surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/10—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve
    • F16K17/105—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve using choking or throttling means to control the fluid operation of the main valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K25/00—Details relating to contact between valve members and seats
    • F16K25/005—Particular materials for seats or closure elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F16F9/465—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall using servo control, the servo pressure being created by the flow of damping fluid, e.g. controlling pressure in a chamber downstream of a pilot passage

Definitions

  • Such a fluid control valve is largely classified into a valve (for example, a pressure reducing valve or the like) which detects a fluid pressure on a secondary side, adjusts a valve opening degree, and restricts a fluid introduction amount from a primary side to control a flow rate or pressure, or the like of a working fluid on the primary side and a valve which detect a fluid pressure of a working fluid and discharges the working fluid to the outside at a predetermined fluid pressure or more to control a flow rate or pressure of the working fluid, that is, a valve having a so-called relief function.
  • a valve for example, a pressure reducing valve or the like
  • the fluid control valve is fluidly connected to a piston chamber and a reservoir chamber of the shock absorber.
  • a piston is disposed in the piston chamber. Accordingly, in the fluid control valve, the valve body is brought into contact with and separated from the valve seat in accordance with a fluid pressure of the piston chamber changing according to the movement of the piston. By using this movement, the shock absorber can control the damping force.
  • the valve body moves while being guided by the valve housing in such a manner that a guide portion of the valve body comes into contact with an inner peripheral surface of the valve housing.
  • contamination may be caught between the inner peripheral surface of the valve housing and the guide portion of the valve body. Accordingly, since resistance to the movement of the valve body is generated, the relief performance of the fluid control valve may deteriorate.
  • the present invention has been made in view of such problems and an object thereof is to provide a fluid control valve that is less likely to malfunction due to contamination.
  • the tapered surface is an inclined surface with respect to an axial direction of the valve body. According to this preferable configuration, since the tapered surface is an inclined surface extending continuously in a linear or curved shape in a cross-sectional view, the valve body can smoothly move with respect to the valve housing.
  • a concave portion extending from the flat surface to the tapered surface is formed in the valve body. According to this preferable configuration, contamination having flowed between the flat surface and the inner surface of the valve housing can be discharged from the tapered surface side through the concave portion.
  • the concave portion is closed on the flat surface. According to this preferable configuration, the valve body can ensure sealing between the inner surface of the valve housing and the outer surface of the valve body.
  • the concave portion is a spiral groove. According to this preferable configuration, the spiral groove that can be configured simply and have high contamination discharge performance is suitable as the concave portion.
  • FIG. 1 is a cross-sectional view illustrating a fluid control valve according to a first embodiment of the present invention.
  • FIG. 2 A is an enlarged explanatory diagram illustrating a main valve of the fluid control valve of the first embodiment
  • FIG. 2 B is an enlarged explanatory diagram illustrating a main valve in which only a flat surface constitutes a guide portion of a valve body of a fluid control valve of a reference example.
  • FIG. 3 is an enlarged view illustrating a main part of the fluid control valve of the first embodiment.
  • FIG. 4 A is an enlarged explanatory diagram illustrating a tilted state of the main valve in the fluid control valve of the first embodiment
  • FIG. 4 B is an enlarged explanatory diagram illustrating a tilted state of the main valve in which only the flat surface constitutes the guide portion of the valve body in the fluid control valve of the reference example.
  • FIG. 5 is a cross-sectional view illustrating a fluid control valve according to a second embodiment of the present invention.
  • a fluid control valve according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 4 . Additionally, this embodiment will be described by exemplifying a fluid control valve used in a shock absorber, but can also be applied to other uses.
  • the top and bottom of the fluid control valve when viewed from the front in FIG. 1 will be described as the top and bottom of the fluid control valve. Specifically, a description will be made such that the lower side of the paper where a main valve 60 is disposed is the lower side of the fluid control valve and the upper side of the paper where a solenoid 80 is disposed as a drive source is the upper side of the fluid control valve.
  • a fluid control valve V 1 of the present invention is fluidly connected to an absorber piston chamber P and a reservoir chamber R of a shock absorber A.
  • the fluid control valve V 1 opens the main valve 60 so that the working fluid flows out from a discharge passage 12 to the reservoir chamber R. Accordingly, the fluid control valve V 1 controls the flow rate of the working fluid flowing from the absorber piston chamber P toward the reservoir chamber R.
  • the fluid control valve V 1 controls the damping force of the shock absorber A.
  • the fluid control valve V 1 mainly includes a valve housing 10 , the pilot valve 50 , the main valve 60 , and a solenoid 80 .
  • the pilot valve 50 is disposed at the upper end portion inside the valve housing 10 . Further, the main valve 60 is disposed below the pilot valve 50 inside the valve housing 10 .
  • the pilot valve 50 includes a pilot valve body 51 and a pilot valve seat 40 a .
  • the pilot valve 50 is opened and closed in such a manner that the pilot valve body 51 is brought into contact with and separated from the pilot valve seat 40 a.
  • the main valve 60 includes a piston 61 which is a valve body and a main valve seat 45 a which is a valve seat.
  • the main valve 60 is opened and closed in such a manner that the piston 61 of the main valve 60 is brought into contact with and separated from the main valve seat 45 a.
  • valve housing 10 is formed in a cylindrical shape with an inner step by a metal material or a resin material.
  • the pilot valve body 51 is inserted into the cylindrical portion 10 a from above in the axial direction.
  • the pilot valve body 51 is formed to have a T-shaped cross-section having a cylindrical portion 52 and a flange portion 53 .
  • the cylindrical portion 52 has a cylindrical shape extending in the axial direction. The lower end portion of the cylindrical portion 52 is seated on the pilot valve seat 40 a.
  • a lower end surface of a rod 83 comes into contact with the upper end portion of the cylindrical portion 52 . Accordingly, the pilot valve body 51 that receives a biasing force of a coil spring 85 comes into press-contact with the rod 83 .
  • the flange portion 53 has an annular plate shape extending radially outward from the upper end portion of the cylindrical portion 52 .
  • a communication passage 53 a is formed in the flange portion 53 to penetrate in the axial direction.
  • the communication passage 53 a communicates the cylindrical portion 10 a of the valve housing 10 with an opening portion 82 b of a center post 82 .
  • the outer peripheral surface of the flange portion 53 is movably formed while being in sliding contact with the inner peripheral surface of the cylindrical portion 10 a of the valve housing 10 . Accordingly, the cylindrical portion 10 a can guide the movement of the pilot valve body 51 .
  • the small-diameter bottomed cylindrical portion 10 b is continuous to the cylindrical portion 10 a and is recessed toward the axially upper side while the inner side of the cylindrical portion 10 a is enlarged in diameter.
  • a pilot valve seat member 40 which is press-inserted from below in the axial direction is integrally fixed to the small-diameter bottomed cylindrical portion 10 b in a substantially sealed state.
  • the pilot valve seat member 40 is formed in a circular plate shape having a plurality of communication passage 41 extending therethrough in the axial direction by a metal material or a resin material.
  • annular convex portion 42 which protrudes in the axially upper side is formed at the center of the upper end portion of the pilot valve seat member 40 .
  • the upper end portion of the annular convex portion 42 is the pilot valve seat 40 a.
  • the piston 61 includes a guide portion 62 , a seal portion 63 , and a spiral groove 64 (see FIG. 2 A ) as a concave portion.
  • the outer peripheral surface of the guide portion 62 is composed of a flat surface 65 and a tapered surface 66 . Additionally, FIG. 2 A illustrates only the configuration of the outer peripheral surface of the piston 61 in order to describe the configuration of the outer peripheral surface of the piston 61 . This also applies to FIGS. 2 B, 3 , 4 A, and 4 B .
  • the tapered surface 66 of this embodiment is an inclined surface having a linear cross-section extending continuously in a direction inclined with respect to the axis. Additionally, the tapered surface may be an inclined surface having a curved cross-section.
  • an inner diameter D 1 of the medium-diameter bottomed cylindrical portion 10 c of the valve housing 10 is slightly larger than a maximum outer diameter D 2 of the guide portion 62 of the piston 61 .
  • a clearance C is formed between an inner peripheral surface 14 of the medium-diameter bottomed cylindrical portion 10 c as the inner surface of the valve housing 10 (hereinafter, simply referred to as the “inner peripheral surface 14 of the valve housing 10 ”) and the flat surface 65 and the tapered surface 66 of the guide portion 62 .
  • the flat surface 65 and the tapered surface 66 of the guide portion 62 are movable while being in sliding contact with the inner peripheral surface 14 of the valve housing 10 . That is, the medium-diameter bottomed cylindrical portion 10 c can guide the movement of the piston 61 .
  • the fluid control valve V 1 can ensure sealing between the inner peripheral surface 14 of the valve housing 10 and the guide portion 62 of the piston 61 .
  • annular convex portion 63 a which protrudes downward in the axial direction is formed at the outer diameter radial lower end portion of the seal portion 63 .
  • the annular convex portion 63 a is seated on the main valve seat 45 a in the valve closed state of the main valve 60 .
  • the spiral groove 64 extends continuously from the axial center portion of the flat surface 65 to the axial center portion of the tapered surface 66 .
  • the spiral groove 64 extends obliquely downward in the circumferential and axial directions from an end portion 64 a closed at the axial center of the flat surface 65 . Then, the spiral groove 64 is closed at an end portion 64 b located at the axial center portion of the tapered surface 66 .
  • the spiral groove 64 is axially closed in the piston 61 . Accordingly, the piston 61 can ensure sealing between the inner peripheral surface 14 of the valve housing 10 and the guide portion 62 of the piston 61 .
  • a coil spring 67 which serves as biasing means for biasing the piston 61 in the closing direction is disposed between the pilot valve seat member 40 and the piston 61 . More specifically, the lower end portion of the coil spring 67 is inserted into the hollow portion 61 a of the piston 61 .
  • a pilot control chamber S is formed in a space inside the small-diameter bottomed cylindrical portion 10 b and the medium-diameter bottomed cylindrical portion 10 c of the valve housing 10 .
  • the pilot control chamber S is defined by the small-diameter bottomed cylindrical portion 10 b , the medium-diameter bottomed cylindrical portion 10 c , the pilot valve seat member 40 , the pilot valve body 51 , and the piston 61 .
  • the large-diameter bottomed cylindrical portion 10 d is continuous to the medium-diameter bottomed cylindrical portion 10 c and is recessed toward the axially upper side while the inside of the medium-diameter bottomed cylindrical portion 10 c is enlarged in diameter.
  • the main valve seat member 45 is formed in an annular plate shape having the inflow passage 11 extending therethrough in the axial direction by a metal material or a resin material.
  • the main valve seat member 45 is press-inserted and fixed to the large-diameter bottomed cylindrical portion 10 d from below in the axial direction through a gasket in a sealed state.
  • the outer surface of the valve housing 10 is provided with a communication groove 10 e having a downward L-shaped cross-section from the upper end of the cylindrical portion 10 a to the side surface thereof.
  • the lower side end portion of the communication groove 10 e is located below an opening portion 81 b of a casing 81 and is opened in the outer radial direction.
  • the pilot side discharge passage 13 includes the cylindrical portion 10 a , the small-diameter bottomed cylindrical portion 10 b , and the communication groove 10 e of the valve housing 10 , the annular convex portion 42 of the pilot valve seat member 40 , the opening portion 81 b of the casing 81 , and the opening portion 82 b of the center post 82 .
  • valve housing 10 is provided with the discharge passage 12 which extends radially outward from the medium-diameter bottomed cylindrical portion 10 c and communicates the inside of the medium-diameter bottomed cylindrical portion 10 c with the reservoir chamber R.
  • the solenoid 80 is connected to the valve housing 10 and applies a driving force to the pilot valve body 51 .
  • the solenoid 80 mainly includes the casing 81 , the center post 82 , the rod 83 , a movable iron core 84 , the coil spring 85 , a coil 86 , a sleeve 87 , and bearings 88 and 89 .
  • the casing 81 includes a stepped cylindrical main body portion 81 a into which the center post 82 is inserted and fixed from below in the axial direction.
  • the center post 82 is formed in a stepped cylindrical shape from a rigid body made of a magnetic material such as iron or silicon steel.
  • the center post 82 includes a cylindrical main body portion 82 a extending in the axial direction.
  • the bearing 89 is inserted and fixed to the main body portion 82 a from above in the axial direction.
  • the rod 83 is inserted and fixed to the movable iron core 84 . Accordingly, when the solenoid 80 is energized, the rod 83 moves to follow the movable iron core 84 moving in the valve closing direction. Accordingly, the rod 83 moves the pilot valve body 51 in the valve closing direction, that is, downward in the axial direction.
  • the upper end portion is inserted through the bearing 88 and the lower end portion is inserted through the bearing 89 .
  • the axial movement of the rod 83 is guided. Therefore, the rod 83 is less likely to be tilted in the radial direction during the axial movement.
  • the coil spring 85 is disposed between the pilot valve seat member 40 and the pilot valve body 51 .
  • the coil spring 85 biases the pilot valve body 51 in the valve opening direction of the pilot valve 50 , that is, in the axially upper side.
  • the coil 86 is an excitation coil wound around the center post 82 through a bobbin.
  • the sleeve 87 is formed in a bottomed cylindrical shape. Further, the bearing 88 guiding the movement of the rod 83 is fitted and fixed to the sleeve 87 .
  • the fluid control valve V 1 in the de-energized state will be described.
  • the pilot valve body 51 of the pilot valve 50 is pressed toward the axially upper side by the biasing force of the coil spring 85 in the de-energized state. Accordingly, the pilot valve body 51 is separated from the pilot valve seat 40 a and the pilot valve 50 is opened.
  • the pilot valve opening degree at this time is the maximum in this embodiment.
  • the cross-sectional area of the communication passage 61 b in the piston 61 is formed to be narrow. Therefore, even when the pressure of the working fluid in the inflow passage 11 increases, the pressure of the working fluid in the pilot control chamber S is less likely to increase in response to the pressure of the working fluid in the inflow passage 11 . Therefore, a differential pressure is generated between the pressure of the working fluid in the inflow passage 11 and the pressure of the working fluid in the pilot control chamber S. As this differential pressure increases, the main valve 60 becomes easier to open.
  • the pressure of the working fluid in the inflow passage 11 is described as the “pressure Pin of the inflow passage 11 ” and the pressure of the working fluid in the pilot control chamber S is described as the “pressure Ps of the pilot control chamber S”.
  • the factor that the differential pressure ⁇ P decreases is that the working fluid passes through the main valve 60 and flows from the discharge passage 12 into the reservoir chamber R so that the pressure Pin of the inflow passage 11 decreases, the working fluid flows from the communication passage 61 b into the pilot control chamber S so that the pressure Pin of the inflow passage 11 decreases, the volume is narrowed due to the movement of the piston 61 so that the pressure Ps of the pilot control chamber S increases, and the like.
  • the opening and closing operation of the main valve 60 will be described in more detail with specific examples.
  • the piston 61 moves in the axially upper side against the biasing force of the coil spring 67 .
  • the valve opening degree of the main valve 60 increases as the pressure Pin (i.e., P 2 ) of the inflow passage 11 approaches a large pressure value P 3 (P 3 >P 2 ).
  • the working fluid in the inflow passage 11 flows from the pilot side discharge passage 13 into the reservoir chamber R in accordance with the operation of the shock absorber A as in the de-energized state. Further, as described above, the working fluid also flows from the discharge passage 12 into the reservoir chamber R depending on the pressure Pin of the inflow passage 11 .
  • the working fluid is less likely to flow from the pilot control chamber S into the pilot side discharge passage 13 as the pilot valve opening degree decreases. Therefore, the differential pressure ⁇ P between the pressure Pin of the inflow passage 11 and the pressure Ps of the pilot control chamber S is less likely to occur and the main valve 60 is less likely to open. That is, the damping force of the shock absorber A can be increased.
  • the damping force of the shock absorber A is minimized. That is, the damping force is controlled to be minimized when the fluid control valve V 1 is in the non-energized state.
  • the differential pressure ⁇ P decreases in a short time as the pilot valve opening degree of the pilot valve 50 decreases. That is, the opening time of the main valve 60 is shortened as the pilot valve opening degree of the pilot valve 50 decreases.
  • the fluid control characteristics of the main valve 60 are controlled according to the pilot valve opening degree of the pilot valve 50 . Accordingly, the fluid control valve V 1 can variably control the damping force of the shock absorber A.
  • the fluid control valve V 1 when the pilot valve 50 is closed in the energized state, the fluid control valve V 1 is in a state in which the working fluid is most difficult to pass through the pilot valve 50 and the main valve 60 is difficult to open. Therefore, the fluid control valve V 1 can maximize the damping force of the shock absorber A.
  • a current value to be energized to the coil 86 constituting the solenoid 80 is set based on input parameters such as vehicle speed, vehicle acceleration/deceleration, steering angle, road surface condition, and sprung load.
  • pilot valve 50 in the open state may be closed by setting a current value equal to or larger than a predetermined value.
  • a normal state in which the piston 61 moves substantially parallel along the axis of the valve housing 10 (hereinafter, simply referred to as a “normal state”) will be described.
  • a state in which the piston 61 moves while being tilted (see FIG. 4 ) will be described.
  • the clearance C having approximately the same dimension is formed over the circumferential direction between the inner peripheral surface 14 of the valve housing 10 and the flat surface 65 of the guide portion 62 of the piston 61 in the normal state.
  • the piston 61 can smoothly move in the axial direction along the axis of the valve housing 10 .
  • the tapered surface 66 of the piston 61 is a smooth surface without unevenness. Therefore, the piston 61 can smoothly move with respect to the valve housing 10 .
  • the tapered surface 66 can guide the movement of the piston 61 . Then, the tapered surface 66 of the piston 61 is a smooth surface without unevenness. Therefore, the piston 61 can smoothly slide on the valve housing 10 .
  • the piston 61 is configured to move while being guided by the inner peripheral surface 14 of the valve housing 10 according to the urging force and differential pressure from the coil spring 67 , the tilting becomes easier than the pilot valve body 51 that moves together with the rod 83 while being guided by the bearings 88 and 89 .
  • the piston 61 can be tilted until the upper end portion of the flat surface 65 and the lower end portion of the tapered surface 66 located on the diagonal line of the upper end portion come into contact with the inner peripheral surface 14 of the valve housing 10 .
  • an axis Ax 2 of the piston 61 indicated by the one-dotted chain line in FIG. 4 A can be tilted up to an angle ⁇ 1 with respect to an axis Ax 1 of the valve housing 10 indicated by the one-dotted chain line in FIG. 4 A .
  • the corners 65 a and 66 a are less likely to come into angular-contact with the inner peripheral surface 14 of the valve housing 10 . Accordingly, in the fluid control valve V 1 , the abrasion of the corners 65 a and 66 a , the damage due to the contact of the corners 65 a and 66 a with respect to the inner peripheral surface 14 , and the like are prevented. Further, in this embodiment, since the tapered surface 66 follows the inner peripheral surface 14 of the valve housing 10 when the piston 61 is tilted, the angular contact is less likely to occur in the corner 66 a than in the corner 65 a.
  • the corner 65 b between the flat surface 65 and the tapered surface 66 is difficult to come into angular-contact with the inner peripheral surface 14 of the valve housing 10 . Accordingly, since the spiral groove 64 crossing a part of the corner 65 b is less likely to come into contact with the inner peripheral surface 14 , damage is suppressed.
  • the minimum outer diameter D 3 of the tapered surface 66 is larger than the outer diameter D 4 of the seal portion 63 (D 3 >D 4 ).
  • the outer radial end of the seal portion 63 is disposed on the inner radial side of a virtual extension line VL 1 of the tapered surface 66 in the radial direction.
  • the piston 61 prevents the seal portion 63 from contacting the inner peripheral surface 14 before the tapered surface 66 contacts the inner peripheral surface 14 of the valve housing 10 . Therefore, the piston 61 is easily tilted within a range in which the seal portion 63 does not easily contact and damage the inner peripheral surface 14 of the valve housing 10 .
  • the tilting of the piston 61 A as a comparative object will be described.
  • the piston 61 A as a comparative object can be tilted until the upper end portion of the flat surface 65 A and the lower end portion of the flat surface 65 A located on the diagonal line of the upper end portion contact the inner peripheral surface 14 of the valve housing 10 .
  • the upper end portion of the flat surface 65 A is a portion which is continuous to a corner 62 Aa between the flat surface 65 A and the upper end surface of the piston 61 A in the flat surface 65 A.
  • the lower end portion of the flat surface 65 A is a portion which is continuous to a corner 62 Ab between the flat surface 65 A and the lower end surface of the guide portion 62 A in the flat surface 65 A.
  • an axis Ax 3 of the piston 61 A indicated by the one-dotted chain line in FIG. 4 B can be tilted up to an angle ⁇ 2 with respect to the axis Ax 1 of the valve housing 10 indicated by the one-dotted chain line in FIG. 4 B .
  • the piston 61 and the piston 61 A may be tilted with the caught contamination as a base point in the caught state.
  • the piston 61 of the present invention in which the tiltable angle ⁇ 1 is large, it is easy to obtain an opening that is sufficient to discharge contamination. Therefore, contamination caught in the piston 61 can be easily discharged.
  • the contamination may move relatively with respect to the pistons 61 and 61 A as the pistons 61 and 61 A move.
  • the piston 61 of the present invention is provided with the spiral groove 64 which is recessed radially inward. Accordingly, contamination flows into the spiral groove 64 and the piston 61 is released from the caught state.
  • the spiral groove 64 can efficiently collect contamination that is displaced in the axial direction.
  • the piston 61 is rotatable in the circumferential direction. Therefore, since the piston 61 rotates in accordance with the axial movement, the spiral groove 64 can efficiently collect contamination that is displaced in the circumferential direction.
  • the spiral groove 64 that extends to the tapered surface 66 tends to introduce contamination into the gap G (see FIG. 2 A ) between the inner peripheral surface 14 of the valve housing 10 and the tapered surface 66 .
  • the gap G is composed of the clearance C and the space H (G>C).
  • the gap G (see FIG. 2 A ) is opened toward the discharge passage 12 .
  • a main valve 160 includes a piston 161 which is a valve body, the main valve seat 45 a , and a bellows 70 .
  • a hollow portion 161 a which is recessed in a cylindrical shape downward in the axial direction is formed in the piston 161 .
  • the hollow portion 161 a is opened upward in the axial direction. Further, the hollow portion 161 a communicates with the inflow passage 11 through the communication passage 61 b formed in the seal portion 63 .
  • the piston 161 includes a base portion 162 and the seal portion 63 .
  • the base portion 162 is formed in a cylindrical shape. Further, the outer diameter of the base portion 162 is smaller than the outer diameter of the seal portion 63 . That is, the seal portion 63 protrudes radially outward in a flange shape from the outer peripheral surface of the base portion 162 .
  • the upper end portion of the bellows 70 is fixed to the corner portion of the medium-diameter bottomed cylindrical portion 10 c of the valve housing 10 . Further, the lower end portion of the bellows 70 is fixed to the outer radial end portion of the seal portion 63 .
  • a sufficient gap is formed between the bellows 70 and the inner peripheral surface 14 of the valve housing 10 so that the bellows 70 is less likely to come into contact with the inner peripheral surface 14 when the piston 161 moves.
  • the piston 161 is movable in the axial direction while being prevented from tilting by the bellows 70 .
  • the fluid control valve includes the pilot valve and the main valve, but the present invention is not limited thereto. That is, the fluid control valve may include only the main valve.
  • a configuration has been described in which the inflow passage and the discharge passage of the housing are formed so that the working fluid flows therethrough, but the present invention is not limited thereto. That is, a connector may be connected to the inflow passage and the discharge passage of the housing, and the working fluid may flow into the housing through the connector. That is, the present invention is not limited to a configuration in which the working fluid directly flows and the inflow passage, and the discharge passage may be formed for the inflow or discharge of the working fluid.
  • valve seat is formed in the valve seat member separated from the valve housing, but the present invention is not limited thereto. That is, the valve seat may be integrally formed with the valve housing.
  • the inner surface of the valve housing may be divided in the circumferential direction by grooves or the like extending axially. That is, the inner surface of the valve housing may be discontinuous in the circumferential direction.
  • valve body is the bottomed cylindrical piston
  • present invention is not limited thereto.
  • its shape may be appropriately changed such that the valve body has a polygonal bottomed cylindrical shape. That is, the flat surface and the tapered surface of the valve body are not limited to the circular shape when viewed in the axial direction and may be the polygonal shape when viewed in the axial direction.
  • the flat surface and the tapered surface of the valve body are continuous in the circumferential direction, but the present invention is not limited thereto.
  • the flat surface and the tapered surface may be divided in the circumferential direction by grooves or the like extending axially. That is, the flat surface and the tapered surface of the valve body may be discontinuous in the circumferential direction.
  • the present invention is not limited thereto. That is, its shape may be appropriately changed such that another tapered surface is formed above the flat surface in the axial direction and a groove extending in the circumferential direction is formed between the flat surface and the tapered surface of the valve body.
  • the spiral groove extends substantially one turn in the circumferential direction, but the present invention is not limited thereto. That is, the spiral groove may extend less than one turn in the circumferential direction. In this case, it is preferable that a plurality of spiral grooves having less than one turn in the circumferential direction are formed in the circumferential direction.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Details Of Valves (AREA)
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